US8708864B2 - Bevel friction ring gearing and method for mounting or producing a bevel friction ring gearing - Google Patents

Bevel friction ring gearing and method for mounting or producing a bevel friction ring gearing Download PDF

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Publication number
US8708864B2
US8708864B2 US12/734,572 US73457208A US8708864B2 US 8708864 B2 US8708864 B2 US 8708864B2 US 73457208 A US73457208 A US 73457208A US 8708864 B2 US8708864 B2 US 8708864B2
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Prior art keywords
friction ring
cone
bevel friction
drive
ring gearing
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US20100261573A1 (en
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Ulrich Rohs
Christoph Draeger
Werner Brandwitte
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/02—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members without members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0487—Friction gearings
    • F16H57/0491—Friction gearings of the cone ring type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49462—Gear making

Definitions

  • the invention on the one hand relates to a bevel friction ring gearing wherein the friction ring can be displaced by means of an adjusting device having a guide on which an adjuster, such as for example an adjusting bridge, is arranged in a free axially displaceable manner.
  • an adjuster such as for example an adjusting bridge
  • the invention relates to a bevel friction ring gearing with a drive cone which is operationally connected with a drive via a positive connection.
  • the invention relates to a bevel friction ring gearing comprising separate fluid spaces for a traction fluid and for a lubricant fluid as well as two gearing sides of which the one is arranged on the side of the cone tip of the drive cone and the other on the side of the cone foot of the drive cone, wherein the fluid space for the lubricant fluid comprises at least two part-spaces and a first part-space is arranged on the one gearing side and a second part space on the other gearing side.
  • the invention also relates to a bevel friction ring gearing with at least two cones which alternatively interact with each other via a friction ring and are clamped together via a pressure device for generating a pressing-on force dependent on the rotational moment, wherein the pressure device comprises rolling bodies which are arranged in corresponding rolling body races of two bodies displaceable relative to each other.
  • the invention relates to a bevel friction ring gearing with at least two cones which interact with each other via a friction ring, wherein at least one of the cones has a separate bearing pin.
  • the invention relates to a bevel friction ring gearing with at least two cones which interact with each other via a friction ring and are clamped together via a pressure device for generating a pressing-on force dependent on the rotational moment, wherein the pressing-on device comprises two bodies displaceable relative to each other. Furthermore, the invention relates to a bevel friction ring gearing with a clutch arranged on the input side and/or a clutch on the output side.
  • the invention relates to a bevel friction ring gearing with at least two cones which interact with each other via a friction ring and are clamped together via a pressing-on device for generating a pressing-on force depending on the rotational moment, wherein the pressing-on device comprises two bodies displaceable relative to each other as well as a spring element.
  • the invention relates to a bevel friction ring gearing with two cones, which interact with each other via a friction ring, and which are clamped together via a pressing-on device for generating a pressing-on force dependent on the rotational moment and is mounted on both sides in bearings which are held in bearing carriers.
  • the invention relates to a method for producing a bevel friction ring gearing as well as a method for assembling a bevel friction ring gearing.
  • a bevel friction ring gearing wherein the friction ring is displaceable via an adjusting device having a guide, on which an adjuster, such as more preferably an adjusting bridge for example for the friction ring, is arranged in a free axially displaceable manner, wherein the bevel friction ring gearing is characterized in that the adjusting device comprises a worm-gear drive.
  • an adjusting device equipped with a worm-gear drive advantageously makes possible a large transmission ratio with relatively small installation space. It also succeeds in rendering the control of the friction ring by means of the worm-gear drive substantially more precise.
  • the term “adjusting device” substantially describes any device by means of which the friction ring can be axially adjusted relative to friction cones of the bevel friction ring gearing.
  • the adjusting device should comprise an adjusting bridge, which has to be stringently designed bridge-like, an adjuster constructed differently can also be employed.
  • the term “adjuster” describes any assembly that guides the friction ring and migrates with said friction ring axially relative to the friction cones depending on the transmission ratio.
  • the invention is substantially advantageous for all types of bevel friction ring gearings, wherein it is particularly immaterial if a cone surface of the friction cones, also called cones in brief, has a straight-line or an arched generatrix.
  • the term “friction ring” describes any device that connects two friction cones of the friction ring gearing more preferably in a frictional manner, wherein the friction ring can axially move forward and backward by means of the adjusting device in a gap of two opposing friction cones and axially to these friction cones.
  • the friction ring engages about one of the two friction cones so that at least a part of one of the two friction cones is arranged within the friction ring.
  • a preferred embodiment version provides that the worm-gear drive acts on an eccentric on which a coupling rod is arranged.
  • Advantageously a space-saving yet operationally safe double reduction can be realised in a constructionally simple manner by means of the worm-gear drive on the one hand and by means of the eccentric in conjunction with the coupling rod on the other hand.
  • the coupling rod acts on an adjusting bridge guide.
  • an end of the coupling rod facing away from the eccentric is fastened to the guide of the adjuster in an articulated or rotationally moveable manner.
  • the coupling rod is additionally spring-loaded, a first overload safety of the bevel friction ring gearing can be accomplished on the adjusting device in a constructionally simple manner.
  • the worm-gear drive is of a design retained by friction.
  • the bevel friction ring gearing can be operated in a particularly energy-saving manner since because of the retention by friction of the worm-gear drive the risk of unintentional adjustment of the friction ring can be prevented.
  • the object of the invention is also solved by a bevel friction ring gearing with a drive cone that is operationally connected with a drive via a positive connection, wherein the operational connection comprises a positive connection that is secured via a central screw.
  • An arrangement of this type substantially has two advantages.
  • the positive connection which is secured via a central screw, produces particularly favourable force distribution so that drive forces can be introduced particularly homogenously into the drive cone of the bevel friction ring gearing by a drive.
  • the central screw which secures the positive connection between the drive cone and the drive, particularly simple assembly of the drive cone on the drive is achieved.
  • the object of the invention is also solved by a bevel friction ring gearing with a drive cone that is operationally connected with a drive via a positive connection, wherein the operational connection comprises a positive connection that is secured via a tensile screw.
  • a tensile screw more preferably a particularly simple tolerance offset especially in the region of the positive connection is achieved with respect to the drive cone and the drive. Even by this alone can the lifespan of the bevel friction ring gearing be substantially increased, more so since a tensile screw can ensure almost optimal and operationally safe assembly with respect to the drive cone and the drive. In particular, possible tolerances during the assembly but also over the lifespan of the bevel friction ring gearing can be offset in an operationally safe and constructionally simple manner.
  • the tensile screw has a clamping length which is greater than the screw diameter, even longer distances between a support region of the screw head of the tensile screw and a threaded bore into which the tensile screw is screwed can be bridged by means of the tensile screw.
  • the stretching properties of the tensile screw are then also applied in a particularly favourable manner.
  • the tensile screw has a clamping length which is substantially greater than the screw diameter the tensile screw can be advantageously passed through a body of a friction cone, more preferably for example through the body of the drive cone, and screwed into a suitable tensile screw thread on the sides of the drive. Because of this, the assembly of the drive cone to the drive can be hugely simplified in addition and a long screw length be provided for the tensile screw.
  • the friction cone, more preferably the drive cone, of the bevel friction ring gearing is dimensioned or configured it can already be sufficient in an advantageous manner if the tensile screw has a clamping length which is at least twice that of the screw diameter of the tensile screw.
  • the tensile screw has a tensile length which is greater than the setting length of the bevel friction ring gearing, in particular its bearing race.
  • a bevel friction ring gearing which comprises separate fluid spaces for a traction fluid and for a lubricant fluid as well as two gearing sides, of which the one is arranged on the side of the cone tip of the drive cone and the other on the side of the cone foot of the drive cone, wherein the fluid space for the lubricant fluid comprises at least two part spaces and a first part space is arranged on the one gearing side and a second part space on the other gearing side and wherein the bevel friction ring gearing is characterized by a lubricant channel which connects the two part spaces and penetrates one of the cones. Because of this, a separate line for lubricant can be advantageously omitted in this manner, which further simplifies the construction of the bevel friction ring gearing.
  • the lubricant channel comprises two cone inlet openings to a rotating channel region with diameters that deviate from each other.
  • a pumping effect can be achieved as a result of which components of an external lubricant pump can be omitted. Because of this, the construction of the bevel friction ring gearing can be advantageously reduced. On the other hand, it can increase the operational safety of the bevel friction ring gearing since additional components of an external lubricant pump can be omitted.
  • a wall of the lubricant channel in the interior of the cone is radially further removed from the cone axis than the wall on the cone inlet opening. Because of this, cleaning of the lubricant due to gravitation can take place since dirt particles of the lubricant can settle within the cone region.
  • a particularly preferred embodiment version in this context also provides that the lubricant channel penetrates a screw. If such a lubricant channel is provided within a screw the screw becomes more thin-walled and can thus be advantageously employed also as tensile screw. Specifically, the screw comprising the lubricant channel can be employed as tensile screw for establishing an operational connection of a positive connection between the drive cone and the drive.
  • the object of the invention is also solved by a further bevel friction ring gearing with at least two cones which interact with each other via a friction ring and which are clamped together via a pressing-on device for generating a pressing-on force dependent on the rotational moment, wherein the pressing-on device comprises rolling bodies which are arranged in corresponding rolling body races of two bodies displaceable relative to each other, and wherein one of the rolling body races is formed in one of the cones.
  • the pressing-on device can more preferably be provided with extraordinarily small tolerances and thus hugely free of play. Assembly is also simplified accordingly.
  • a further solution of the object of the invention proposes a bevel friction ring gearing with at least two cones which interact with each other via a friction ring, wherein at least one of the cones has a separate bearing pin, wherein the separate bearing pin is connected with the cone via a seat divided in two.
  • an extraordinarily even forced distribution on the seat divided in two can be achieved between the separate bearing pin and the cone if both part seats have a rotation-symmetrical seat surface. Because of this, the separate bearing pin and the cone corresponding therewith can be produced without problems and matched to each other.
  • both part seats are arranged at a different axial height of the corresponding cone.
  • a first part seat is arranged axially outside with respect to the cone and designed radially larger than the second part seat arranged axially further inside, as a result of which the construction of this arrangement can be simplified yet again. Because of this, the corresponding cone can be advantageously produced with a lesser material quantity, for example by means of a forging process.
  • a bevel friction ring gearing which is characterized by at least one forged cone.
  • a forged cone can be provided particularly light in weight, with high quality and corresponding longevity and accordingly is advantageous even independent of the remaining features of the present invention.
  • the object of the invention is also solved by a method for producing a bevel friction ring gearing wherein at least one of the cones comprises at least one forged assembly.
  • the assembly of the cone that provides the cone surface is advantageously forged. More preferably a forged cone surface can excel through particularly high strength characteristics and thus improve the lifespan and the operational safety of the present bevel friction ring gearing yet again.
  • a special embodiment version in this context provides that all cones comprise forged assemblies as a result of which the operational safety of the bevel friction ring gearing as a whole can be further increased.
  • a further advantageous embodiment version provides that the cone and the separate bearing pin are connected with each other via a press fit. Because of this, a simple, quick and operationally safe connection can more preferably be executed between the separate bearing pin and the corresponding cone.
  • the object of the invention is also solved by a method for the assembly of a bevel friction ring gearing, wherein a separate bearing pin and a cone are pressed together.
  • connection types can also be selected.
  • cone and the separate bearing pin are welded together.
  • an, alternative method version provides that the separate bearing pin and a cone are welded together following the pressing together.
  • a further solution of the present object provides a bevel friction ring gearing with at least two cones which interact with each other via a friction ring and are clamped together via a pressing-on device for generating a pressing-on force dependent on the rotational moment, wherein the pressing-on device comprises two bodies that can be displaced relative to each other, wherein at least one of the displaceable bodies is mounted on one of the cones by way of a needle bearing.
  • More preferably mounting the displaceable body on one of the cones by means of a needle bearing can guarantee an extraordinarily good safeguard against tilting moments so that the bevel friction ring gearing can boast particularly high operational safety and a long lifespan.
  • the needle bearing is designed split, so that at least two needle bearing races with respect to a cone axis of rotation are arranged axially next to each other.
  • a bevel friction ring gearing with a clutch arranged on an input side and/or a clutch arranged on an output side, wherein the clutch is hydraulically activated.
  • a hydraulically activated clutch more preferably has the advantage that assemblies for the hydraulic activation can be placed in a space-saving manner in a clear space between the cone axes of rotation and the installation space for the adjusting device, for example the worm-gear drive.
  • Another solution of the object proposes a bevel friction ring gearing with at least two cones which interact via a friction ring and which are clamped together via a pressing-on device for generating a pressing-on force dependent on the rotational moment, wherein the pressing-on device comprises two bodies that are displaceable relative to each other and a spring element, and wherein the bevel friction ring gearing is characterized in that the spring element can be removed without removing the displaceable bodies.
  • the object of the invention is also solved by a method of a bevel friction ring gearing, wherein all cones are mounted on both sides in their bearing carriers and their respective spring element is mounted thereafter.
  • the cones are easier to adjust because of this, since at least up to this assembly stage assembly can be performed without pre-stress.
  • a bevel friction ring gearing with at least two cones which interact with each other via a friction ring, which cones are clamped together via a pressing-on device for generating a pressing-on force dependent on the rotational moment and which on both sides are mounted in bearings which are held in bearing carriers, wherein both bearing carriers are designed in one piece.
  • a design of the bearing carriers so selected produces fewer tolerance problems, as a result of which more preferably the manufacture and the assembly of the bevel friction ring gearing can be simplified.
  • the operational safety and the lifespan of such a bevel friction ring gearing also benefit from fewer tolerance problems.
  • displaceable bodies can be ideally adjusted without any critical pre-stress, assembly of a bevel friction ring gearing is substantially facilitated.
  • FIG. 1 schematically a longitudinal sectional view of a bevel friction ring gearing
  • FIG. 2 an exploded drawing of the drive cone with a thrust shoulder for securing the friction ring against critical thrust in the event of a fault of the adjusting device of the bevel friction ring gearing according to FIG. 1 ;
  • FIG. 3 the drive cone according to FIG. 2 in the assembled state
  • FIG. 4 an exploded view drawing of the output cone with a thrust shoulder for securing the friction ring against critical thrust in the event of a fault of an adjusting device of the bevel friction ring gearing according to FIG. 1 ;
  • FIG. 5 the output cone according to FIG. 5 in the assembled state
  • FIG. 6 schematically a view of a worm-gear drive of the adjusting device of the bevel friction ring gearing according to FIG. 1 .
  • the bevel friction ring gearing 1 shown in FIG. 1 comprises as first substantial components a drive cone 2 , an output cone 3 and a friction ring 4 , wherein the friction ring 4 , engaging about the drive cone 2 , can be moved forward and backward in a gap 5 between the drive cone 2 and the output cone 3 according to the double arrow 6 .
  • the drive cone 2 can rotate about a first axis of rotation 7
  • the output cone 3 can rotate about a further axis of rotation 8 .
  • the friction ring 4 is displaceably fastened or held within the cone friction ring gearing 1 by means of an adjusting device 9 .
  • the adjusting device 9 substantially comprises an adjusting bridge 10 which is effective as adjuster and comprises a guide arm 11 with a plurality of guide wheels 12 (merely one is exemplarily shown), by means of which the friction ring 4 can be held and guided within the bevel friction ring gearing 1 .
  • the adjusting bridge 10 can be moved along an adjusting bridge guide 13 , so that the friction ring 4 can be moved forward and backward in the gap 5 according to the double arrow 6 .
  • the adjusting bridge guide 13 with this exemplary embodiment runs in alignment with the gap 5 , as a result of which the friction ring 4 can be precisely moved along and within the gap 5 .
  • the adjusting device 9 comprises a drive 14 which is designed as worm-gear drive 15 .
  • the construction of the drive 14 of the present bevel friction ring gearing 1 can be very clearly retraced by means of the representation according to FIG. 6 .
  • the worm-gear drive 15 is fastened to a housing wall 16 of the bevel friction ring gearing 1 and drives a worm retained by friction 17 as worm-gear drive.
  • the worm retained by friction 17 in turn is engaged with an eccentric coupling member 18 to which a spring-loaded coupling rod 19 is fastened.
  • the spring-loaded coupling rod 19 has a spring 19 a and is connected With the eccentric coupling member 18 at an articulation point 20 .
  • the spring-loaded coupling rod 19 is connected to the adjusting bridge guide 13 at its end 21 facing away from the eccentric coupling member 18 .
  • the eccentric coupling member 18 can be swiveled about an eccentric shaft 22 which in turn moves the spring-loaded coupling rod 19 .
  • This movement of the spring-loaded coupling rod 19 is transmitted to the adjusting bridge guide 13 , as a result of which migrating of the adjusting bridge 10 together with the friction ring 4 can be triggered or also stopped again.
  • At least a double reduction in terms of the drive 14 is achieved by means of such a worm-gear drive 15 with a screw 17 retained by friction and an eccentric 18 as well as a spring-loaded coupling rod 19 , so that the adjusting bridge guide 13 can be adjusted with minimal drive distances in an operationally safe manner.
  • the spring-loaded coupling rod 19 additionally has the advantage that with it an overload safety of the bevel friction ring gearing 1 can be realised in a constructionally simple manner, as a result of which the spring-loaded coupling rod 19 more preferably the adjusting bridge guide 13 during a critical operating state can always adjust the bevel friction ring gearing 1 by means of a predetermined spring force in such a manner that emergency running characteristics can always materialise automatically on the bevel friction ring gearing 1 with respect to the friction ring 4 and the two friction cones 2 and 3 .
  • the screw 17 retained by friction specifically offers the advantage that the friction ring 4 can be held in its position in a particularly energy saving manner since the retention by friction of the screw 17 retained by friction can be advantageously selected in such a manner that adjustment of the eccentric 18 cannot be performed without the worm-gear drive 15 or only under certain circumstances.
  • the bevel friction ring gearing 1 can be substantially subdivided into a first gearing side 30 and a second gearing side 31 . While the first gearing side 30 is substantially assigned bearing components and a cone space arranged between the first gearing side 30 and the second gearing side 31 is substantially assigned the two friction cones 2 and 3 , the friction ring 4 with the adjusting device 9 as first most important components of the bevel friction ring gearing, a clutch 33 with a gyrating mass device 34 on the drive end 32 and a differential gearing 36 on the output end 35 can be assigned to the second gearing side 31 .
  • the clutch 33 used here is already well known from the prior art so that in this regard merely a central release 33 A a release piston 33 B corresponding to said central release, a release cylinder 33 C and a release spring 33 D of suitably strong design for this purpose are numbered.
  • first lubricant part space 37 On the first gearing side 30 a first lubricant part space 37 is formed while on the second gearing side 31 a second lubricant part space 38 is formed. Both lubricant part spaces 37 and 38 belong to a first fluid space 39 of the bevel friction ring gearing 1 and are spatially connected with each other by means of a lubricant channel 40 . Within the first fluid space 39 and thus also within the lubricant part spaces 37 and 38 is located a lubricant fluid which more preferably can lubricate the rolling bearing devices of the bevel friction ring gearing 1 .
  • a traction fluid of the bevel friction ring gearing 1 which in terms of traction between the two friction cones 2 and 3 and the friction ring 4 can act in a supportive manner is located in a further fluid space 41 , which is formed in the cone space and which for example can also comprise the gap 5 of the bevel friction ring gearing 1 .
  • additional external feed and/or discharge lines for the lubricant fluid can be omitted by means of the present lubricant channel 40 , more preferably if the lubricant channel 40 penetrates at least the drive cone 2 .
  • the lubricant channel 40 itself continues through a central tensile screw 42 by means of which more preferably a positive connection 43 between the drive cone 2 and an output device 44 of the bevel friction ring gearing is secured. Through the central tensile screw 42 constructed in such a manner the lubricant channel 40 extends to a region 45 in which a hydraulic lubricant fluid feed 46 can terminate.
  • the central tensile screw 42 is furnished with a clamping length which is at least twice the size of the screw diameter of the tensile screw 42 , wherein the clamping length can be described as substantially greater than the screw diameter of the tensile screw 42 . More preferably the tensile screw 42 has a tensile length which is greater than the setting length of the bevel friction ring gearing 1 .
  • a spur toothing 47 of the drive cone 2 can always be adequately held in engagement with complementary toothing (not numbered here) of the drive device 44 .
  • a lubricant channel in the tensile screw can be omitted.
  • the output cone 3 furthermore comprises a pressing-on device 50 (see especially FIGS. 4 and 5 ), by means of which a pressing-on force dependent on the rotational moment can be generated.
  • the pressing-on device 50 comprises rolling bodies 51 which are arranged in corresponding rolling body races 52 and 53 of two bodies 54 and 55 displaceable relative to each other.
  • the first rolling body race 52 is inserted directly within the output cone 3 so that drive cone 3 an displaceable body 54 are realised by one assembly and a particularly play-free pressing-on device 50 is realised on the bevel friction ring gearing 1 .
  • the pressing-on device 50 comprises a spring element 56 which can build up a pre-stress in the pressing-on device 50 .
  • the special construction of the drive cone 2 can be particularly taken from the representations according to FIGS. 2 and 3 .
  • the drive cone 2 comprises a separate bearing pin 60 having a first bearing seat 61 and a second bearing seat 62 , so that the separate bearing pin 60 altogether can be fastened in the interior 63 of the drive cone 2 in a manner that is particularly secure against tilting. If applicable, the separate bearing pin 60 once it has been pressed into the drive cone 2 can be additionally welded, as a result of which the separate bearing pin 60 and the drive cone 2 are additionally sealed relative to each other in a fluid-tight manner.
  • the first bearing seat 61 has a larger diameter than the second bearing seat 62 , but both bearing seats 61 and 62 have a rotation-symmetrical seat surface.
  • the two bearing seats 61 and 62 are axially arranged at different heights, good leverage conditions are obtained so that the drive cone 2 can be pressed on to the separate bearing pin 60 in a manner that is extraordinarily secure against tilting.
  • a rotating insert 64 for reducing the lubricant fluid quantity, more preferably the lubricant fluid quantity rotated in the cone, can be inserted.
  • a centrifugal separator 66 is additionally provided by means of which dirt particles from the lubricant fluid can be trapped.
  • the rotating insert 64 is given a larger diameter at the first end 65 than at a further end 67 , which is located opposite the first end 65 .
  • the first end 65 of the rotating insert 64 is additionally assigned an additional rotating device 68 for further increasing an opening diameter more preferably of the lubricant channel 40 .
  • the drive cone 2 as forged component comprises a forged cone surface 70 which ends in a drive cone tip 71 in the region of a thrust shoulder 72 .
  • the thrust shoulder 72 is provided for securing the friction ring 4 , so that the friction ring 4 cannot leave the cone surface 70 in the event of a fault of the bevel friction ring gearing 1 .
  • a thrust shoulder 72 is missing on the drive cone 2 , since on the drive cone 3 located opposite a corresponding additional thrust shoulder 80 (see particularly FIGS. 4 and 5 ) is arranged, which can take up the thrust of the friction ring 4 in a critical operating situation of the bevel friction ring gearing 1 .
  • each drive cone 2 and 3 respectively only have exactly one thrust shoulder 72 and 80 respectively.
  • the second pressing-on body 55 which comprises the second rolling body race 53 for the rolling bodies 51 is located in the interior 82 of the drive cone 3 .
  • a first rolling body race 52 corresponding with the second rolling body race 53 however is directly integrated in the drive cone 3 , so that the drive cone 3 itself directly forms the first pressing-on body 54 .
  • the spring device 56 is likewise inserted into the interior of the drive cone 3 , wherein the spring device 56 substantially comprises a spring holder 83 and a multiplicity 84 of disc springs, which are slid on to the spring holder 83 as well as a spacer ring 85 .
  • the spring device 56 is secured within the output cone 3 by means of a locking washer 86 .
  • the output cone 3 likewise as forged component comprises a further forged cone surface 87 so that the output cone 3 is also highly loadable.
  • Both friction cones 2 and 3 are mounted in a special manner on a housing 1 A of the bevel friction ring gearing 1 , so that more preferably assembly of the friction cones 2 and 3 can be advantageously carried out.
  • the drive cone 2 is mounted with a first drive cone bearing 88 and with a second drive cone bearing 89 .
  • the output cone 3 is mounted with a first output cone bearing 90 and a second output cone bearing 91 .
  • the first drive cone bearing 88 and the first output cone bearing 90 are jointly located on the first gearing side 30 .
  • the second drive cone bearing 89 and the second output cone bearing 91 are jointly arranged on the second gearing side 31 .
  • first drive cone bearing 88 and the first output cone bearing 90 are both held by a first common bearing carrier 92 of the cone friction ring gearing 1 .
  • second drive cone bearing 89 and the second output cone bearing 91 are both held by a further common bearing carrier 93 of the bevel friction ring gearing 1 . Because of this, substantially fewer tolerance problems are incurred so that both friction cones 2 and 3 can be accurately positioned relative to each other. This is true more so since both the first common bearing carrier 92 as well as the additional common bearing carrier 93 are each formed in one piece.
  • bearing eyes (not numbered here) for the corresponding bearing pairings 88 and 90 as well as 89 and 91 with the bearing carriers 92 and 93 respectively can be provided substantially more accurately on the bevel friction ring gearing 1 .
  • the additional common bearing carrier 93 can be jointly formed with the housing wall 16 described above, as a result of which the bevel friction ring gearing 1 can be configured stiffer yet.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Gears, Cams (AREA)
  • Gear Transmission (AREA)
  • Pressure Welding/Diffusion-Bonding (AREA)
  • General Details Of Gearings (AREA)
  • Mechanical Operated Clutches (AREA)
US12/734,572 2007-11-27 2008-11-27 Bevel friction ring gearing and method for mounting or producing a bevel friction ring gearing Expired - Fee Related US8708864B2 (en)

Applications Claiming Priority (4)

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DE102007057354.7 2007-11-27
DE102007057354 2007-11-27
DE102007057354 2007-11-27
PCT/DE2008/001966 WO2009068012A2 (de) 2007-11-27 2008-11-27 Kegelreibringgetriebe sowie verfahren zur montage bzw. herstellung eines kegelreibringgetriebes

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PCT/DE2008/001966 A-371-Of-International WO2009068012A2 (de) 2007-11-27 2008-11-27 Kegelreibringgetriebe sowie verfahren zur montage bzw. herstellung eines kegelreibringgetriebes

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US14/189,202 Continuation US20140171256A1 (en) 2007-11-27 2014-02-25 Bevel friction ring gearing and method for mounting or producing a bevel friction ring gearing

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US20100261573A1 US20100261573A1 (en) 2010-10-14
US8708864B2 true US8708864B2 (en) 2014-04-29

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US12/734,572 Expired - Fee Related US8708864B2 (en) 2007-11-27 2008-11-27 Bevel friction ring gearing and method for mounting or producing a bevel friction ring gearing
US14/189,202 Abandoned US20140171256A1 (en) 2007-11-27 2014-02-25 Bevel friction ring gearing and method for mounting or producing a bevel friction ring gearing

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US14/189,202 Abandoned US20140171256A1 (en) 2007-11-27 2014-02-25 Bevel friction ring gearing and method for mounting or producing a bevel friction ring gearing

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US (2) US8708864B2 (ja)
EP (1) EP2215380B1 (ja)
JP (2) JP5562248B2 (ja)
CN (2) CN103398148B (ja)
AT (1) ATE511037T1 (ja)
BR (1) BRPI0819068A2 (ja)
DE (1) DE112008003116A5 (ja)
ES (1) ES2366990T3 (ja)
RU (1) RU2529087C2 (ja)
WO (1) WO2009068012A2 (ja)

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JP4924511B2 (ja) * 2008-03-31 2012-04-25 アイシン・エィ・ダブリュ株式会社 動力伝達装置
EP2146113B1 (de) * 2008-07-16 2011-11-02 Ulrich Rohs Reibringgetriebe mit einem Reibring und Verfahren zum Herstellen eines Reibkegels
JP2011202754A (ja) * 2010-03-26 2011-10-13 Aisin Aw Co Ltd 動力伝達装置
CN102562980A (zh) * 2012-02-24 2012-07-11 北京理工大学 一种液压加紧式牵引传动装置
JP5875427B2 (ja) * 2012-03-23 2016-03-02 ジヤトコ株式会社 コーンリング型無段変速機
DE102014012537A1 (de) 2014-08-28 2016-03-03 Ulrich Rohs Untersetzungsgetriebe, Verfahren zur Untersetzung einer Drehbewegung sowie Verwendung eines Untersetzungsgetriebes sowie eines Untersetzungsverfahrens
WO2016029907A1 (de) 2014-08-28 2016-03-03 Ulrich Rohs Kegelreibringgetriebe, verwendung eines untersetzungsgetriebes sowie verfahren zur anstellung des reibrings eines kegelreibringgetriebes
CN112846677A (zh) * 2020-12-07 2021-05-28 南昌齿轮锻造厂 一种带凸台的主动螺旋锥齿轮立锻和粗精车工艺
CN115924831A (zh) * 2022-11-30 2023-04-07 杭州莱和生物技术有限公司 一种传染病检测用取样装置的密封结构及方法

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US2807171A (en) 1955-09-14 1957-09-24 Wyckoff Theodore Automatic transmission
US2898775A (en) * 1955-02-08 1959-08-11 E R D Lab Inc Variable gear drive
WO2004061336A1 (de) 2003-01-06 2004-07-22 Ulrich Rohs Anpresseinrichtung zum verspannen zweier getriebeglieder und getriebe mit einer derartigen anpresseinrichtung sowie verfahren zum betrieb eines derartigen reibgetriebes
WO2006012892A2 (de) 2004-08-06 2006-02-09 Ulrich Rohs Reibringgetriebe mit zwei voneinander um einen spalt beabstandeten wälzkörpern
EA007706B1 (ru) 2002-09-30 2006-12-29 Ульрих Рос Передаточное устройство
JP2009126289A (ja) 2007-11-21 2009-06-11 Nissan Motor Co Ltd 車両のスライドドア用ガイドレール構造
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US2038731A (en) * 1933-09-13 1936-04-28 Foote Gear Works Inc Driving mechanism
US2898775A (en) * 1955-02-08 1959-08-11 E R D Lab Inc Variable gear drive
US2807171A (en) 1955-09-14 1957-09-24 Wyckoff Theodore Automatic transmission
EA007706B1 (ru) 2002-09-30 2006-12-29 Ульрих Рос Передаточное устройство
US7559868B2 (en) * 2002-09-30 2009-07-14 Ulrich Rohs Epicyclic gear
WO2004061336A1 (de) 2003-01-06 2004-07-22 Ulrich Rohs Anpresseinrichtung zum verspannen zweier getriebeglieder und getriebe mit einer derartigen anpresseinrichtung sowie verfahren zum betrieb eines derartigen reibgetriebes
US7553254B2 (en) 2003-01-06 2009-06-30 Ulrich Rohs Pressing device for tensioning two gearing elements, gearing provided with a pressing device of this type, and method for operating such a friction gearing
WO2006012892A2 (de) 2004-08-06 2006-02-09 Ulrich Rohs Reibringgetriebe mit zwei voneinander um einen spalt beabstandeten wälzkörpern
US20090118073A1 (en) 2004-08-06 2009-05-07 Ulrich Rohs Friction-Ring Transmission Having Two Roller Bodies Spaced Apart From One Another By a Gap
JP2009126289A (ja) 2007-11-21 2009-06-11 Nissan Motor Co Ltd 車両のスライドドア用ガイドレール構造

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Also Published As

Publication number Publication date
ATE511037T1 (de) 2011-06-15
EP2215380A2 (de) 2010-08-11
CN103398148A (zh) 2013-11-20
WO2009068012A3 (de) 2009-11-05
JP6103251B2 (ja) 2017-03-29
WO2009068012A2 (de) 2009-06-04
RU2529087C2 (ru) 2014-09-27
CN102007320A (zh) 2011-04-06
JP2014159880A (ja) 2014-09-04
RU2010118490A (ru) 2012-01-10
CN102007320B (zh) 2013-11-20
CN103398148B (zh) 2018-10-02
BRPI0819068A2 (pt) 2015-12-22
JP5562248B2 (ja) 2014-07-30
US20100261573A1 (en) 2010-10-14
DE112008003116A5 (de) 2010-08-19
EP2215380B1 (de) 2011-05-25
ES2366990T3 (es) 2011-10-27
JP2011504983A (ja) 2011-02-17
US20140171256A1 (en) 2014-06-19

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